CN102216643A - Air damper - Google Patents
Air damper Download PDFInfo
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- CN102216643A CN102216643A CN2009801462931A CN200980146293A CN102216643A CN 102216643 A CN102216643 A CN 102216643A CN 2009801462931 A CN2009801462931 A CN 2009801462931A CN 200980146293 A CN200980146293 A CN 200980146293A CN 102216643 A CN102216643 A CN 102216643A
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- Prior art keywords
- cap
- cylindrical shell
- damping hole
- diameter
- air damper
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
- F16F9/0209—Telescopic
- F16F9/0218—Mono-tubular units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
- F16F9/0209—Telescopic
- F16F9/0281—Details
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3235—Constructional features of cylinders
- F16F9/3242—Constructional features of cylinders of cylinder ends, e.g. caps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/3415—Special valve constructions; Shape or construction of throttling passages characterised by comprising plastics, elastomeric or porous elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Damping Devices (AREA)
- Vehicle Step Arrangements And Article Storage (AREA)
- Actuator (AREA)
Abstract
An air damper which, according to an input load, provides an appropriate damping force. An air damper is provided with the following: a tubular cylinder (1) having opposite ends open; a piston (2) moving in the cylinder (1); and a cap (3) for closing the opening in one end of the cylinder (1). The cylinder (1) has an annular seal surface (4) on the peripheral surface of the opening of the cylinder (1). The cap is mounted to the opening side of the cylinder (1) so as to be movable or deformable in the direction of the axis of the cylinder (1). The cap makes contact with and is separated from the seal surface (4) by a pressure variation caused by movement of the piston (2) in the cylinder (1). A first orifice (14) is formed in a base plate (12) of the cap. During operation of the first orifice (14), a second orifice having a smaller inflow area than the first orifice (14) is defined between the cap (3) and the cylinder (1).
Description
Technical field
The present invention relates to a kind of cartridge type air damper, it is used for for example glove compartment of Motor Vehicle.
Background technique
Although do not specifically illustrate, the conventional air damper of this class comprises: tubular barrel, and it locates all openings two ends; Piston, it moves in cylindrical shell; And, cap, an end opening portion of its closed cylinder.In cylindrical shell, at one end the inner peripheral surface side of opening portion forms annular sealing surface, and, cap has dish shape substrate and annular seal flange, dish shape substrate is installed in the end opening portion of cylindrical shell, and with along the moving axially of cylindrical shell, the annular seal flange extends radially to protrude from substrate, in substrate, offer a damping hole (for example, referring to patent documentation 1).
Therefore, be used at this air damper under the situation of Motor Vehicle glove compartment the cylindrical shell rotary way being fixed to the instrument panel side, and, terminal part (stretching out from the cylindrical shell the other end end) rotary way of piston rod is fixed to the glove compartment side.Then, when present dynasty opens direction and moves glove compartment, piston rod is pulled out from the inside of cylindrical shell gradually, and piston moves in equidirectional in cylindrical shell.Yet, at this very moment, owing to allowing the cap substrate to move because of cylinder internal pressure changes, by this, the sealing flange of cap is closely contacted with the sealing surface of cylindrical shell fully, and the flow resistance by the air by an above-mentioned damping hole guarantees that glove compartment moves to open mode lentamente.
On the contrary, when present dynasty's closed position moves glove compartment, in response to moving of glove compartment piston rod is advanced cylindrical shell gradually, piston also moves at equidirectional in cylindrical shell.On the other hand, at this moment,, the substrate of cap is in the opposite direction moved by the air in the cylindrical shell,, thereby cause the air in the cylindrical shell outwards to overflow so that impel sealing flange to move apart the sealing surface of cylindrical shell by the variation in pressure in the cylindrical shell.By this, promote the closing operation of glove compartment.
Patent documentation 1:JP-2000-065116-A
Summary of the invention
Invent problem to be solved
Yet, for conventional air damper, even input changing load, the inlet-duct area of damping hole is always constant, this brings following problem, for example, when air damper is used in the glove compartment that weight is housed and damper when being used in the glove compartment that light thing is housed, between the two there be than big-difference the opening speed of glove compartment.
The measure of dealing with problems
In order to solve intrinsic problem in the above-mentioned conventional air damper effectively, the present invention is proposed.
Based on claim 1, the air damper that claim 2 of the present invention provides is characterised in that: the adjacent portion, and it is present between cap and the cylindrical shell, and the diameter of adjacent portion is less than the diameter of sealing surface, but greater than the diameter of first damping hole; Groove, it is formed on the approximal surface of adjacent portion, and groove extends in the external diameter direction of adjacent portion; And, second damping hole, it is limited by groove.
Based on claim 1, the air damper that claim 3 of the present invention provides is characterised in that: the adjacent portion, and it is present between cap and the cylindrical shell, and the diameter of adjacent portion is less than the diameter of sealing surface, but greater than the diameter of first damping hole; Trickle concaveconvex shape, it is formed on the approximal surface of adjacent portion; And, second damping hole, it is limited by trickle concaveconvex shape.
Based on claim 1, the air damper that claim 4 of the present invention provides is characterised in that: the adjacent portion, and it is present between cap and the cylindrical shell, and the diameter of adjacent portion is less than the diameter of sealing surface, but greater than the diameter of first damping hole; Through hole, it is formed in the adjacent portion, and through hole is connected with inner barrel; And, second damping hole, it is limited by this through hole.
Based on claim 2 or claim 3, the air damper that claim 5 of the present invention provides is characterised in that: the adjacent portion has the concavity space, and the diameter in concavity space is greater than the diameter of first damping hole.
Based on claim 1, the air damper that claim 6 of the present invention provides is characterised in that: the adjacent portion, and it is present between cap and the cylindrical shell, and the diameter of adjacent portion is less than the diameter of sealing surface, but greater than the diameter of first damping hole; The adjacent portion has the concavity space, and the diameter in concavity space is greater than the diameter of first damping hole; And, through hole, it is formed in the bottom or sidepiece in concavity space.
Based on claim 1, the air damper that claim 7 of the present invention provides is characterised in that: channel shaped is formed in the cap side.
Based on claim 3, the air damper that claim 8 of the present invention provides is characterised in that: trickle concaveconvex shape is formed at the cap side.
Based on claim 1 arbitrary claim to the claim 8, the air damper that claim 9 of the present invention provides is characterised in that: first damping hole is positioned on the axis of cylindrical shell.
Based on claim 2 or claim 3, the air damper that claim 10 of the present invention provides is characterised in that: cap is formed by soft material.
The advantage of invention
Therefore, in claim 1 of the present invention, since when input load is low only first damping hole work, and input load works second damping hole so that increase braking force when higher, like this, can control air damper, thus can not cause because of the weight of dress object the glove compartment opening speed than big-difference.
Second damping hole can be limited simply by groove in claim 2 of the present invention, and if second damping hole is limited by the hole, mould has pin shape profile.Yet, under the situation that adopts the moulding of groove form,, can when guaranteeing the second damping hole mould strength, make the diameter of second damping hole as far as possible little owing to only need on mould, to be provided with rib shape protuberance.
In claim 3 of the present invention, limit second damping hole with trickle concaveconvex shape, compare when limiting second damping hole with hole and groove, can further improve the intensity of mould.
In claim 4 of the present invention, limit second damping hole with through hole, make second damping hole be difficult to be subjected to the influence of cap or cylindrical shell in abutting connection with attitude, so, can guarantee the stable operation of second damping hole.
In claim 5 of the present invention, flow to air convection current in a spiral manner in the concavity space the concavity space from first damping hole, and be difficult for flowing to second damping hole, thereby increased flow resistance, by this, increase braking force.
In claim 6 of the present invention, in the bottom in concavity space or sidepiece, through hole is set, similarly, make through hole not be vulnerable to the influence in abutting connection with attitude of cap or cylindrical shell, so, can guarantee the stable operation of second damping hole.In addition, because via the concavity space of diameter greater than the first damping hole diameter, second damping hole that through hole limits is connected with first damping hole easily, has improved assembly manipulation.In addition, flow to the air convection current the concavity space in a spiral manner in concavity space from first damping hole, and be difficult for flowing to second damping hole, by this, because flow resistance is increased, and braking force is increased.
In claim 7 of the present invention, be formed in the cap side owing to limit the channel shaped of second damping hole, for general cylindrical shell, can provide multiple air damper with low cost only by changing cap with different braking power.
In claim 8 of the present invention, be formed at the cap side owing to limit the trickle concaveconvex shape of second damping hole, for general cylindrical shell, can provide multiple air damper with low cost only by changing cap with different braking power.
In claim 9 of the present invention, because first damping hole is positioned on the axis of cylindrical shell, no longer need to carry out the circumferential alignment of cap during the assembling cap, be convenient to assembly manipulation.
In claim 10 of the present invention, because cap is formed by soft material, allow cap can sting into groove or trickle concaveconvex shape, and, allow the distortion of groove and trickle concaveconvex shape elastic type, thereby, braking force can be changed as required.
Description of drawings
Fig. 1 is the front view that illustrates according to the air damper local excision of first embodiment of the invention.
Fig. 2 is the sectional view that the cylindrical shell major component is shown.
Fig. 3 A is the sectional view that cap is shown, and Fig. 3 B is the front view that cap is shown.
Fig. 4 is the major component sectional view that air damper assembling back state is shown.
Fig. 5 is the major component sectional view that the input low load condition is shown.
Fig. 6 is the major component sectional view that the input higher load condition is shown.
Fig. 7 illustrates the major component sectional view that allows the outside overflow status of air in the cylindrical shell.
Fig. 8 is the front view that is illustrated in cap set on second embodiment's air damper.
Fig. 9 is the major component sectional view that illustrates according to the 3rd embodiment's air damper.
Embodiment
Air damper of the present invention comprises: tubular barrel, and it locates all openings two ends; Piston, it moves in cylindrical shell; And, cap, one end opening portion of its closed cylinder, cylindrical shell has the annular sealing surface that is formed on the above-mentioned end opening portion side face, cap is installed on an above-mentioned end opening portion side of cylindrical shell, with moving axially or be out of shape along cylindrical shell, thereby, according to because piston moves the variation in pressure cause in cylindrical shell, make cap contact or be separated with it with sealing surface, offer first damping hole in the substrate of cap, this air damper is characterised in that: in first damping hole operation period, limit second damping hole between cap and cylindrical shell, the inlet-duct area of second damping hole is less than the inlet-duct area of first damping hole.Adopt this structure, when the input changing load, automatically switch to second damping hole from first damping hole, so that suitable braking force is provided.
(first embodiment)
Below, based on preferred embodiment, describe the present invention.As shown in Figure 1, comprise according to first embodiment's air damper: tubular barrel 1, it is at place, two ends opening; Piston 2, it moves in cylindrical shell 1; And, cap 3, an end opening portion of its closed cylinder 1.
In addition, as shown in Figure 2, in cylindrical shell 1, in the inner peripheral surface side of the one end opening 1a of portion side, form annular sealing surface 4, in response to variation in pressure, sealing surface 4 moves, to contact or to be separated with it with the sealing flange 13 (hereinafter explanation) of cap 3.In addition, base plate limits sealing surface 4, is formed with the adjacent pipe 5 at the end at base plate central part place, and adjacent pipe 5 is stretched out towards cap 3 sides, and has the concavity space 6 towards interior side opening; Simultaneously, continuous mode forms outward extending prolongation wall 7 on the periphery of sealing surface 4.In prolonging wall 7, form a plurality of locking apertures 8 and excision portion 9.Although do not specifically illustrate, the other end opening portion side of cylindrical shell 1 has the form that can insert logical piston rod 10.Should be noted that sealing surface 4 can be formed at the outer circumferential face side of a 1a of end opening portion.
Piston 2 and piston rod 10 global formations, and by means of the bias spring pressure of coil compression springs 11, elastic type makes piston 2 put towards the 1a of an end opening portion lateral deviation of cylindrical shell 1.
In addition, as shown in FIG., in cap 3, real estate 12a is towards adjacent pipe 5 terminal parts of cylindrical shell 1, the recessed step of real estate 12a, thereby, when high load is imported into air damper, make the terminal part of single order concave type real estate 12a and adjacent pipe 5 adjacent to each other, by this, between cap 3 and cylindrical shell 1, the adjacent portion occurs.On the other hand, on single order concave type real estate 12a, form single groove 17, its external diameter direction in the adjacent portion is stretched out.Under the state of adjacency between the terminal part of single order concave type real estate 12a and adjacent pipe 5, by utilizing single groove 17 energetically, can form second damping hole, its inlet-duct area is less than the inlet-duct area of first damping hole 14.In addition, if do not have load or low-load input air damper is only arranged, the adjacent portion is set for, can form gap 18 between the terminal part of single order concave type real estate 12a and adjacent pipe 5.
Therefore, when the assembling as the damper of above-mentioned structure, coil compression springs 11, piston rod 10 and piston 2 are injected its inside from the 1a of an end opening portion side of cylindrical shell 1, afterwards, location piece 16 with prolong at cylindrical shell 1 under the situation that formed excision portion 9 aligns in the wall 7, cap 3 compressed into prolonged wall 7.Then, the locking plate 15 on the cap 3 movably is locked in the locking aperture 8 that is formed at prolongation wall 7, by this, as shown in Figure 4, can easily assembles the one-way fashion air damper.
Then, when air damper is actually used in the glove compartment of Motor Vehicle, although do not specifically illustrate, conventional air damper is the same with adopting, via installation sheet 19 cylindrical shell 1 rotary way is being fixed under the situation of instrument panel side, can is only needing piston rod 10 to be fixed to the glove compartment side with rotary way via the mounting hole 20 that is arranged at piston rod 10 terminal parts.
Like this, when present dynasty opens direction and moves glove compartment, piston rod 10 is pulled out from the inside of cylindrical shell 1 gradually.In cylindrical shell 1 inside, piston 2 moves in the direction identical with piston rod 10 pull-out directions, yet, meanwhile, cap 3 is also attempted to move to be drawn in cylindrical shell 1 inside, at this moment, and when the load of importing air damper is low, the travelling speed of piston 2 is also slower, the state that negative pressure sharply increases in the cylindrical shell 1 do not occur.So, as shown in Figure 5, the amount of travel of cap 3 is less, and, fully assurance can limit under the situation in gap 18 between the terminal part of the single order concave type real estate 12a of cap 3 and adjacent pipe 5, and the sealing flange 13 of cap 3 closely is attached to the sealing surface 4 of cylindrical shell 1 fully as sucker.Like this, by means of the flow resistance of the air by first damping hole 14 (in cap 3 substrates 12, offering) only, guarantee that glove compartment slowly moves towards opening direction.
Yet, when the load of importing air damper is higher, when being contained on the glove compartment as weight, negative pressure in the cylindrical shell 1 increases rapidly, and cap 3 significantly moves in cylindrical shell 1, as shown in Figure 6, by this, make the terminal part of single order concave type real estate 12a and adjacent pipe 5 adjacent fully each other.For this reason, at this moment, because groove 17 has limited (formation) second damping hole of inlet-duct area less than first damping hole, 14 inlet-duct areas, make damping hole switch to second damping hole from first damping hole automatically, the result, by means of the flow resistance of the air that passes through second damping hole, can control the opening speed of glove compartment as required.In addition, when this automatic switchover took place, the effect of block was played in the existence of adjacent pipe 5, thereby, can prevent effectively that cap 3 from dropping into cylindrical shell 1 inside.
In addition, the air that flows to from first damping hole 14 is in case be imported into concavity space 6 (its diameter is greater than the diameter of first damping hole 14 of the adjacent pipe 5 of cylindrical shell 1), just convection current in a spiral manner.So, make the air of such importing be difficult to flow to the second damping hole side, this has increased flow resistance, by this, braking force is increased.By in cap 3, forming groove 17, advantageously allow to use general cylindrical shell 1, only change cap 3 and provide multiple air damper with different braking power with low cost.In addition,, no longer need its circumferential alignment during cap 3 assemblings, by this, advantageously be convenient to assembly manipulation because first damping hole 14 is positioned on the axis of cylindrical shell 1.In addition, in contrast, under groove 17 was formed at situation in the adjacent portion on cylindrical shell 1 side, because cap 3 forms by the soft thermoplastic elastomer, soft cap 3 groove of nipping by this, can change braking force as required.
Adopt in first embodiment and limit the structure of (formation) second damping hole by groove 17, if limit second damping hole with the hole, forming the used mould in this hole is pin shape thing, so under the too thin situation of pin shape mould, mould fractures easily.Yet,, can only need on mould, to be provided with rib shape protuberance if also keep limiting the structure of second damping hole with groove 17.So, moulding groove 17 easily not only, and, can when guaranteeing mould strength, make the diameter of second damping hole as far as possible little.
On the contrary, when when closing direction moves glove compartment,, piston rod 10 is advanced cylindrical shell gradually in response to moving of glove compartment.So, although piston 2 also moves at equidirectional in cylindrical shell 1, at this moment, as shown in Figure 7, the result who changes as cylindrical shell 1 internal pressure by the air that is accumulated in the cylindrical shell, helps the sealing flange 13 of cap 3 to move apart the sealing surface 4 of cylindrical shell 1, thereby, impel the air that is accumulated in the cylindrical shell 1 outwards to overflow.So, allow piston 2 not return its initial position with having resistance, by this, promoted the closing operation of glove compartment.
In first embodiment, although second damping hole is by the constituting of groove 17 and concavity space 6, second damping hole also can be defined as concavity space 6 is not set.In this case, groove 17 need directly be communicated with first damping hole 14, to extend to the outside diameter of adjacent portion.So groove 17 is preferably formed in cap 3 sides but not is formed at cylindrical shell 1 side, because needn't control assembly precision like this.
(second embodiment)
Then, air damper according to second embodiment is described.About essential characteristic,, and adopted first embodiment's structure with similar according to first embodiment's air damper according to second embodiment's air damper.Yet, the different structures that are as shown in Figure 8 of second embodiment's air damper and first embodiment's air damper, wherein, continuous mode forms trickle concaveconvex shape 21 on the whole single order concave type real estate 12a of cap 3, thereby, under the adjacent a kind of like this state of the terminal surface of single order concave type real estate 12a that makes cap 3 and adjacent pipe 5, replace first embodiment's groove 17, can limit second damping hole by concaveconvex shape 21.Much less, the inlet-duct area of second damping hole that is limited by trickle concaveconvex shape 21 is less than the inlet-duct area of first damping hole 14.
The result, similarly, adopt second embodiment, when the load of input air damper hanged down, the amount of travel of cap 3 was also less, by this, between the terminal part of the single order concave type real estate 12a of cap 3 and adjacent pipe 5, fully guarantee to be limited with under the state in gap 18, the sealing flange 13 complete close attachment that make cap are in the sealing surface 4 of cylindrical shell 1, by this, guarantee that glove compartment slowly moves opening direction.
When the load of input air damper is higher, when being contained on the glove compartment as weight, cap 3 significantly moves in cylindrical shell 1, this makes single order concave type real estate 12a terminal part complete and adjacent pipe 5 adjacent, by this, at this moment, limit second damping hole of inlet-duct area by trickle concaveconvex shape 21 less than first damping hole, 14 inlet-duct areas.So, like this damping hole being automatically switched to second damping hole from first damping hole, the result in this case, similarly, can control the opening speed of glove compartment by the flow resistance of the air that passes through second damping hole as required.
In addition, similarly, adopt second embodiment, similar with first embodiment, the air that flows to from first damping hole 14, in case be imported into the concavity space 6 of the adjacent pipe 5 of cylindrical shell 1, just convection current in a spiral manner by this, makes this part air be difficult to flow to the second damping hole side, this has increased flow resistance, and has improved braking force.In addition, form trickle concaveconvex shape 21 on the cap 3, allow to use a general cylindrical shell 1, provide multiple air damper with low cost with different braking power by changing cap 3.In addition, in contrast, when on the adjacent portion of cylindrical shell 1 side, forming trickle concaveconvex shape 21, because cap 3 forms by the soft thermoplastic elastomer, the soft cap 3 trickle concaveconvex shape 21 of nipping, thereby, can change braking force as required.
In addition, adopt second embodiment, owing to adopted the structure that limits second damping hole with trickle concaveconvex shape 21, than limiting second damping hole with hole or groove 17, the more easily moulding of trickle concaveconvex shape 21, and, can when guaranteeing mould strength, make the diameter of second damping hole as far as possible little.
(the 3rd embodiment)
At last, air damper according to the 3rd embodiment is described.Although in first embodiment and second embodiment's air damper, the mechanism that limits second damper is formed at cap 3 sides, but in the 3rd embodiment, as shown in Figure 9, in the bottom or sidepiece of adjacent pipe 5, form the through hole 22 that is connected with cylindrical shell 1 inside, thereby, under the terminal part of single order concave type real estate 12a that makes cap 3 and adjacent pipe 5 a kind of like this state adjacent to each other, through hole 22 limits second damping hole thus, to replace groove 17 among first embodiment and the trickle concaveconvex shape 21 among second embodiment.Much less, the inlet-duct area of second damping hole that is limited by through hole 22 is also less than the inlet-duct area of first damping hole 14.
The result, similarly, adopt the 3rd embodiment, when the load of input air damper hanged down, the amount of travel of cap 3 was also less, by this, be limited with under a kind of like this state in gap 18 abundant assurance the between the terminal part of single order concave type real estate 12a and adjacent pipe 5, the sealing flange 13 complete close attachment that make cap are in the sealing surface 4 of cylindrical shell 1, by this, guarantee that glove compartment slowly moves opening direction.
When the load of input air damper higher, when being contained on the glove compartment as weight, cap 3 significantly moves in cylindrical shell 1, this makes its single order concave type real estate 12a terminal part complete and adjacent pipe 5 adjacent, by this, at this moment, limit second damping hole of inlet-duct area by through hole 22 less than first damping hole, 14 inlet-duct areas.So, like this damping hole being automatically switched to second damping hole from first damping hole, the result in this case, similarly, can control the opening speed of glove compartment by means of the flow resistance of the air that passes through second damping hole as required.
In addition, similarly, adopt the 3rd embodiment, similar with first embodiment, the air that flows to from first damping hole 14, in case be imported into the concavity space 6 of the adjacent pipe 5 of cylindrical shell 1, just convection current in a spiral manner by this, makes this part air be difficult to flow to the second damping hole side, this has increased flow resistance, and has improved braking force.In addition, in this 3rd embodiment, because through hole 22 is not to be formed at cap 3 sides, but be formed in the bottom or sidepiece of adjacent pipe 5, make second damping hole be difficult to be subjected to the influence of the attitude of cap adjacent to each other 3 and cylindrical shell 1, thereby, stable operation can be guaranteed.
Industrial usability
Owing to can change brake force according to the variation of input load according to air damper of the present invention, even high load capacity input, also can suitably show the brake force that the high load capacity with the input air damper is complementary, be applied at this air damper will obtain good effect in the situation of glove compartment etc. of motor vehicle.
Description of reference numerals
1 cylindrical shell 12a single order concave type real estate
1a one end opening section 13 sealing flanges
2 pistons, 14 first damping holes
3 caps, 15 locking plates
4 sealing surfaces, 16 spacers
5 in abutting connection with pipe 17 grooves
18 gaps, 6 concavity spaces
7 prolong wall 19 installation sheets
8 lock holes, 20 installing holes
9 excision portions, 21 trickle concaveconvex shapes
10 piston rods, 22 through holes
The external diameter of 11 coil compression springs, 23 adjacent portions
12 substrates
Claims (10)
1. air damper comprises:
Tubular barrel, all openings are located in two end;
Piston, it moves in described cylindrical shell; And
Cap, it seals an end opening portion of described cylindrical shell,
Wherein, described cylindrical shell has the annular sealing surface on the side face that is formed at a described end opening portion,
Wherein, described cap is installed on an end opening portion side of described cylindrical shell, so that described cap is along the axially movable or deformable of described cylindrical shell,
Wherein, along with the mobile variation in pressure that cause of described piston in described cylindrical shell, described cap contacts or is separated with it with described sealing surface, and
Wherein, in the substrate of described cap, offer first damping hole,
It is characterized in that:
In the operation period of described first damping hole, between described cap and described cylindrical shell, limit second damping hole, the inlet-duct area of described second damping hole is less than the inlet-duct area of described first damping hole.
2. air damper according to claim 1 is characterized in that:
The adjacent portion, it is present between described cap and the described cylindrical shell, and the diameter of described adjacent portion is less than the diameter of described sealing surface, but greater than the diameter of described first damping hole;
Groove, it is formed on the approximal surface of described adjacent portion, and described groove extends in the external diameter direction of described adjacent portion; And
Second damping hole, it is limited by described groove.
3. air damper according to claim 1 is characterized in that:
The adjacent portion, it is present between described cap and the described cylindrical shell, and the diameter of described adjacent portion is less than the diameter of described sealing surface, but greater than the diameter of described first damping hole;
Trickle concaveconvex shape, it is formed on the approximal surface of described adjacent portion; And
Second damping hole, it is limited by described trickle concaveconvex shape.
4. air damper according to claim 1 is characterized in that:
The adjacent portion, it is present between described cap and the described cylindrical shell, and the diameter of described adjacent portion is less than the diameter of described sealing surface, but greater than the diameter of described first damping hole;
Through hole, it is formed in the described adjacent portion, and described through hole is connected with the inside of described cylindrical shell; And
Second damping hole, it is limited by described through hole.
5. according to claim 2 or the described air damper of claim 3, it is characterized in that:
Described adjacent portion has the concavity space, and the diameter in described concavity space is greater than the diameter of described first damping hole.
6. air damper according to claim 1 is characterized in that:
The adjacent portion, it is present between described cap and the described cylindrical shell, and the diameter of described adjacent portion is less than the diameter of described sealing surface, but greater than the diameter of described first damping hole;
Described adjacent portion has the concavity space, and the diameter in described concavity space is greater than the diameter of described first damping hole; And
Through hole, it is formed in the bottom or sidepiece in described concavity space.
7. air damper according to claim 2 is characterized in that:
Described channel shaped is formed in the cap side.
8. air damper according to claim 3 is characterized in that:
Described trickle concaveconvex shape is formed at the cap side.
9. according to claim 1 described air damper of each claim to the claim 8, it is characterized in that:
Described first damping hole is positioned on the axis of described cylindrical shell.
10. according to claim 2 or the described air damper of claim 3, it is characterized in that:
Described cap is formed by soft material.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008304783 | 2008-11-28 | ||
| JP2008-304783 | 2008-11-28 | ||
| PCT/JP2009/004117 WO2010061500A1 (en) | 2008-11-28 | 2009-08-26 | Air damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102216643A true CN102216643A (en) | 2011-10-12 |
| CN102216643B CN102216643B (en) | 2014-02-26 |
Family
ID=42225392
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200980146293.1A Active CN102216643B (en) | 2008-11-28 | 2009-08-26 | Air damper |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US8528708B2 (en) |
| JP (1) | JP5274578B2 (en) |
| KR (1) | KR101490965B1 (en) |
| CN (1) | CN102216643B (en) |
| DE (1) | DE112009003489T5 (en) |
| FR (1) | FR2939174B1 (en) |
| WO (1) | WO2010061500A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111971489A (en) * | 2018-03-28 | 2020-11-20 | 百乐仕株式会社 | Damper |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9156325B2 (en) * | 2008-03-19 | 2015-10-13 | Fox Factory, Inc. | Methods and apparatus for vehicle suspension having multiple gas volumes |
| US9702176B2 (en) | 2014-07-07 | 2017-07-11 | Itt Manufacturing Enterprises Llc | Spring loaded actuator assembly |
| US9500249B2 (en) * | 2015-03-09 | 2016-11-22 | The Boeing Company | Energy absorbing link |
| JP6786707B2 (en) * | 2017-03-23 | 2020-11-18 | 株式会社パイオラックス | Air damper |
| US20210078697A1 (en) * | 2019-09-13 | 2021-03-18 | Shake N Bake Llc | Shock absorbing foot piece for small apparatus |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US5104098A (en) * | 1988-10-24 | 1992-04-14 | Nifco, Inc. | Cylinder type air damper |
| GB2267948A (en) * | 1992-06-17 | 1993-12-22 | Illinois Tool Works | Air dampers |
| US5697477A (en) * | 1994-10-07 | 1997-12-16 | Nifco Inc. | Air damper |
| JP2006283877A (en) * | 2005-03-31 | 2006-10-19 | Piolax Inc | Air damper |
| CN101074711A (en) * | 2007-05-09 | 2007-11-21 | 朱洪纲 | Reducer for absorbing vibration energy refrigeration |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US4535876A (en) | 1983-03-16 | 1985-08-20 | Tayco Developments, Inc. | Shock absorber construction |
| US4792128A (en) * | 1988-03-08 | 1988-12-20 | Power Components, Inc. | No grow gas spring |
| US5275387A (en) * | 1992-04-09 | 1994-01-04 | Power Components, Inc. | Gas spring |
| JPH08105482A (en) * | 1994-10-07 | 1996-04-23 | Nifco Inc | Air damper |
| US6062352A (en) | 1998-08-24 | 2000-05-16 | Piolax, Inc. | Air damper |
| JP3312244B2 (en) | 1998-08-24 | 2002-08-05 | 株式会社パイオラックス | Air damper |
| US6199838B1 (en) * | 1998-10-27 | 2001-03-13 | Diebolt International, Inc. | Gas spring filler valve |
-
2009
- 2009-08-26 JP JP2010540296A patent/JP5274578B2/en active Active
- 2009-08-26 US US12/998,608 patent/US8528708B2/en active Active
- 2009-08-26 KR KR1020117012223A patent/KR101490965B1/en active IP Right Grant
- 2009-08-26 WO PCT/JP2009/004117 patent/WO2010061500A1/en active Application Filing
- 2009-08-26 DE DE112009003489T patent/DE112009003489T5/en active Pending
- 2009-08-26 CN CN200980146293.1A patent/CN102216643B/en active Active
- 2009-11-27 FR FR0958433A patent/FR2939174B1/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5104098A (en) * | 1988-10-24 | 1992-04-14 | Nifco, Inc. | Cylinder type air damper |
| GB2267948A (en) * | 1992-06-17 | 1993-12-22 | Illinois Tool Works | Air dampers |
| US5697477A (en) * | 1994-10-07 | 1997-12-16 | Nifco Inc. | Air damper |
| JP2006283877A (en) * | 2005-03-31 | 2006-10-19 | Piolax Inc | Air damper |
| CN101074711A (en) * | 2007-05-09 | 2007-11-21 | 朱洪纲 | Reducer for absorbing vibration energy refrigeration |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111971489A (en) * | 2018-03-28 | 2020-11-20 | 百乐仕株式会社 | Damper |
| US11459812B2 (en) | 2018-03-28 | 2022-10-04 | Piolax, Inc. | Damper |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112009003489T5 (en) | 2012-08-02 |
| FR2939174B1 (en) | 2014-01-03 |
| US8528708B2 (en) | 2013-09-10 |
| JP5274578B2 (en) | 2013-08-28 |
| JPWO2010061500A1 (en) | 2012-04-19 |
| WO2010061500A1 (en) | 2010-06-03 |
| US20110209954A1 (en) | 2011-09-01 |
| CN102216643B (en) | 2014-02-26 |
| FR2939174A1 (en) | 2010-06-04 |
| KR20110095871A (en) | 2011-08-25 |
| KR101490965B1 (en) | 2015-02-06 |
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